EP3182213B2 - Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk - Google Patents

Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk Download PDF

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Publication number
EP3182213B2
EP3182213B2 EP15200453.7A EP15200453A EP3182213B2 EP 3182213 B2 EP3182213 B2 EP 3182213B2 EP 15200453 A EP15200453 A EP 15200453A EP 3182213 B2 EP3182213 B2 EP 3182213B2
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EP
European Patent Office
Prior art keywords
balance
resiliently flexible
flexible blades
mechanical oscillator
mounting base
Prior art date
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Application number
EP15200453.7A
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English (en)
French (fr)
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EP3182213B1 (de
EP3182213A1 (de
Inventor
Nicolò Robuschi
Giulio Papi
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Manufacture dHorlogerie Audemars Piguet SA
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Manufacture dHorlogerie Audemars Piguet SA
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Application filed by Manufacture dHorlogerie Audemars Piguet SA filed Critical Manufacture dHorlogerie Audemars Piguet SA
Priority to ES15200453T priority Critical patent/ES2698115T3/es
Priority to EP15200453.7A priority patent/EP3182213B2/de
Priority to US16/061,939 priority patent/US20180372150A1/en
Priority to PCT/EP2016/081132 priority patent/WO2017102916A1/fr
Priority to JP2018531329A priority patent/JP2018537684A/ja
Priority to CN201680077919.8A priority patent/CN108475039A/zh
Publication of EP3182213A1 publication Critical patent/EP3182213A1/de
Publication of EP3182213B1 publication Critical patent/EP3182213B1/de
Application granted granted Critical
Priority to HK18112680.0A priority patent/HK1253383A1/zh
Publication of EP3182213B2 publication Critical patent/EP3182213B2/de
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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/12—Pivotal connections incorporating flexible connections, e.g. leaf springs
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/063—Balance construction
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/10—Oscillators with torsion strips or springs acting in the same manner as torsion strips, e.g. weight oscillating in a horizontal plane
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2370/00—Apparatus relating to physics, e.g. instruments

Definitions

  • the present invention relates to the field of mechanical watchmaking. More precisely, it relates to a mechanism for adjusting an average speed in a clockwork movement, as well as a clockwork movement.
  • a driving member such as a barrel spring supplies the driving energy, which a finishing gear transmits to the escape wheel of an escapement interacting with a mechanical oscillator.
  • the speeds of the gears in the finishing gear are all proportional to a rotational speed, which is the average rotational speed of the escape wheel.
  • the average speed of rotation of this escape wheel is imposed by the oscillations of the mechanical oscillator. More precisely, the function of the mechanical oscillator is to provide the rate at which the angular steps of the escape wheel follow one another. This rate must be as stable as possible.
  • the object of the invention is at least to enable a reduction or even elimination of the friction occurring at the level of the support of a balance wheel of a mechanical oscillator to be obtained without the accuracy of a clockwork movement operating at the aid of this mechanical oscillator is too affected by the degree of winding of the motor organ.
  • This adjustment mechanism is more precisely a mechanism for adjusting an average speed in a clockwork movement and comprises an escape wheel and a mechanical oscillator.
  • This mechanical oscillator comprises a balance and several elastically flexible blades which are elastically flexible in a plane of oscillation and which carry and recall the balance so that this balance oscillates angularly in the plane of oscillation.
  • the adjustment mechanism comprises an anchor comprising two rigid paddles which are rigidly integral with the balance and arranged to cooperate alternately with a toothing of the escape wheel when the balance oscillates angularly.
  • the driving torque of the escape wheel does not or practically not interfere with the oscillations of the balance, except during the impulse phases. It has been found that this makes the accuracy of the time count is less dependent on the degree of winding of the motor unit.
  • the elastically flexible blades can easily be arranged so that the oscillations of the balance have an amplitude compatible with the use of an escapement, the anchor of which comprises two rigid paddles rigidly secured to the balance.
  • the adjustment mechanism defined above can incorporate one or more other advantageous characteristics, individually or in combination, in particular among those specified below.
  • each pallet comprises an upstream side forming a rest surface for successively locking teeth of the downstream toothing against a driving torque for driving the escape wheel, each pallet comprising an end surface forming an impulse surface for successively receiving impulses from the teeth.
  • each resting surface curves towards the other resting surface.
  • the accuracy of the time counting is most often even less dependent on the degree of winding of the motor member.
  • each resting surface curves towards the other resting surface so as to be able to slide on a tooth of the toothing, during an angular oscillation of the balance, while causing no or substantially no rotational movement of the wheel. exhaust.
  • the accuracy of the time counting is even less dependent on the degree of winding of the motor member.
  • each rest surface has a substantially constant curvature in the direction of its length and has a center of curvature substantially positioned always at the same place, substantially on an axis of virtual swing of the balance.
  • the accuracy of the time counting is even less dependent on the degree of winding of the motor member.
  • the mechanical oscillator comprises a mounting base.
  • At least part of the elastically flexible blades each have an end rigidly joined to the mounting base.
  • at least part of the elastically flexible blades each have an end rigidly joined to the balance.
  • the mechanical oscillator comprises a mounting base, while at least a first and a second elastically flexible blade among the elastically flexible blades each have two opposite ends, namely a first end rigidly united to the base assembly and a second end, at least a third and a fourth elastically flexible blade among the elastically flexible blades each comprising two opposite ends, namely a first end rigidly united to the balance and a second end, and that the second ends of the first, at least second, third and fourth elastically flexible blades are rigidly joined to each other.
  • the return torque which the first, second, third and fourth elastically flexible blades together exert on the balance is generally proportional to the angular displacement of the balance from a neutral position and that this contributes to a good isochronism of the mechanical oscillator. Still in the case defined in the previous paragraph, it is easy to obtain that the oscillations of the balance have an amplitude compatible with the use of an escapement with rubbing rest.
  • the second ends of the first, second, third and fourth elastically flexible blades are rigidly joined to each other by a coupling part.
  • the first ends of the first and second elastically flexible blades are angularly offset from one another by an angle of between 80 ° and 150 °, around an axis perpendicular to the plane of oscillation and centered on the part. coupling, the first ends of the third and fourth elastically flexible blades being angularly offset from each other by an angle of between 80 ° and 150 °, around the axis perpendicular to the plane of oscillation and centered on the coupling part.
  • the first ends of the first and second elastically flexible blades are angularly offset from each other by an angle of the order of 120 °, around the axis perpendicular to the plane of oscillation and centered on the part. coupling, the first ends of the third and fourth elastically flexible blades being angularly offset from each other by an angle of the order of 120 °, around the axis perpendicular to the plane of oscillation and centered on the coupling part.
  • the mechanical oscillator comprises a mounting base, while at least part of the mounting base, at least part of the balance and the elastically flexible blades are part of the same part of a one piece.
  • a compact solution can be obtained. It can be done at a reduced cost insofar as the elastically flexible blades, at least part of the mounting base and at least part of the balance can be produced at the same time with the same device (s).
  • a reduction in components assemble can also be obtained.
  • increased precision can be obtained as to the geometry of the assembly, in particular when the one-piece part is produced by means of the DRIE process or the LiGA process.
  • At least part of the mounting base, at least part of the balance and the elastically flexible blades are made of silicon and / or of silicon oxide.
  • the second ends of the first, second, third and fourth elastically flexible blades are rigidly joined to each other by a coupling part through which passes a virtual pivot axis of the balance.
  • the coupling part is located substantially at an equal distance from the first ends of the first, second, third and fourth elastically flexible blades.
  • the balance has a center of gravity located substantially at the coupling part.
  • the first and second elastically flexible blades are substantially symmetrical to each other with respect to a plane.
  • the third and fourth elastically flexible blades are substantially symmetrical to each other with respect to this plane.
  • the first and third elastically flexible blades extend in the same plane perpendicular to the plane of oscillation.
  • the second and fourth elastically flexible blades extend in the same plane perpendicular to the plane of oscillation.
  • the mounting base comprises two stops which are end-of-travel stops for the balance and which define a maximum angular travel of the balance by preventing this balance from going beyond two opposite ends of this maximum angular travel.
  • the two elastically flexible blades are protected against damage resulting from too great a deformation, such as deformation following an impact.
  • the balance comprises two opposite wings and a cross member connecting these two wings to one another, at least part of the elastically flexible blades each comprising one end rigidly joined to said cross member.
  • the mounting base or an equivalent thereof may not be surrounded by the balance, which offers greater design freedom.
  • Another subject of the invention is a clockwork movement, comprising a driving member, a gear train driven by the driving member, and an adjustment mechanism as defined above, the escape wheel being driven by the gear train.
  • a timepiece movement according to one embodiment of the invention comprises a barrel 1, of which a driving member, not shown, such as a spiral spring, produces a driving torque and which, because of this driving torque, drives a gear train. finishing 2.
  • This finishing gear 2 in turn drives an escapement mobile 3, which forms part of an escapement 4 further comprising an anchor 5.
  • This anchor 5 is carried by the balance 6 of a mechanical oscillator 7.
  • a plate not shown or a frame of another type carries the barrel 1, the exhaust mobile 3, the mechanical oscillator 7 and the finishing gear 2, the wheels of which can be held in place in a known manner by itself, by bridges also not shown.
  • the exhaust mobile 3 comprises a pinion 8, which meshes with a wheel of the finishing gear 2.
  • the escapement 4 and the mechanical oscillator 7 are associated so as to form together a mechanism 9 for adjusting an average speed of rotation in the clockwork movement of the figure 1 .
  • the exhaust 4 is a friction-rest exhaust.
  • its escapement mobile 3 comprises, in addition to the pinion 8, an escape wheel 11 comprising a peripheral toothing 12, which is provided to cooperate alternately with an input pallet 13 and an outlet pallet 14 of the anchor 5.
  • the set of teeth 12 consists of a succession of triangular teeth 15, each of which ends with a substantially pointed free end.
  • the mechanical oscillator 7 is symmetrical with respect to a plane of symmetry P 1 . Essentially, that is to say if we except weights 16 and 17 carried by its balance 6, this mechanical oscillator 7 is flattened and extends in a plane P 4 perpendicular to the plane of symmetry P 1 . This plane P 4 is the plane of the sheet at the figure 3 .
  • the mechanical oscillator 7 comprises a fixed mounting base 18, which has the shape of a plate and which is intended to be rigidly fixed to the plate of the clockwork movement, by means of screws (not shown) or other control members. fixation. Through holes 19 for the passage of such screws are drilled in the mounting base 18, in the direction of its thickness.
  • This mounting base 18 has two lateral fingers, which form angular end-of-travel stops 20 for the balance 6 and which are directed towards a cross member 21 of this balance 6.
  • An elastic articulation constituting the mechanical oscillator 7 comprises a first elastically flexible blade 23a, a second elastically flexible blade 23a, a third elastically flexible blade 23b, a fourth elastically flexible blade 23b and a coupling part 27.
  • This elastic articulation connects the mounting base 18 at the cross member 21. It carries the balance 6 while being itself carried by the mounting base 18.
  • the mounting base 18, the elastically flexible blades 23a and 23b, the coupling part 27 and the balance 6 with the exception of the weights 16 and 17 are part of a single piece.
  • the elastically flexible blades 23a are substantially symmetrical to one another with respect to the plane of symmetry P 1 . The same is true of the elastically flexible blades 23b.
  • Each elastically flexible blade 23a has a first end 24, at the level of which it is connected rigidly to the mounting base 18. In other words, each elastically flexible blade 23a is joined to the mounting base 18 by a connection. recessed type.
  • Each elastically flexible blade 23b has a first end 25, at the level of which it is rigidly connected to the cross member 21. In other words, each elastically flexible blade 23b is joined to the cross member 21 by a connection of the recessed type.
  • each of the elastically flexible blades 23a and 23b has a second end 26 and connects to the ridged coupling part 27 at this second end 26.
  • the second ends 26 of the blades elastically flexible 23a and 23b are rigidly joined together.
  • Each of the elastically flexible blades 23a and 23b extends along a regulated surface all of the generatrices of which are perpendicular to the plane P 4 of the mechanical oscillator 7.
  • the blades 23a and 23b are thus elastically flexible in the plane P 4 and they allow angular oscillations of the balance 6 in this plane P 4 , around a virtual pivot axis X 2 -X ' 2 .
  • the plane P 4 is therefore the plane of oscillation of the balance 6.
  • each of the elastically flexible blades 23a and 23b is rectilinear, which however could not be the case.
  • the first elastically flexible blade 23a and the third elastically flexible blade 23b extend in the same plane P 2 , which might not be the case.
  • the second elastically flexible blade 23a and the fourth elastically flexible blade 23b extend in the same plane P 3 , which might not be the case.
  • the planes P 2 and P 3 are the above-mentioned ruled surfaces and are perpendicular to the plane P 4 .
  • the coupling part 27 is located at a distance from the first ends 24 and 25. Preferably, it is more precisely at an equal distance from these first ends 24 and 25.
  • the virtual pivot axis X 2 -X ' 2 is centered. on the coupling part 27. It remains substantially in the plane of symmetry P 1 when the balance 6 oscillates.
  • the elastically flexible blades 23a and 23b elastically return this balance 6 to a neutral position. , which is the one that the balance 6 occupies at figures 2 to 5 .
  • the angle ⁇ is the angle between the planes P 2 and P 3 . More precisely, this angle ⁇ is the angle of which the first end 24 of one of the elastically flexible blades 23a and the first end 24 of the other elastically flexible blade 23a are angularly offset from each other around an axis which merges with the virtual pivot axis X 2 -X ' 2 in the example shown and which is more precisely the axis perpendicular to the plane P 4 and centered on the coupling part 27.
  • the angle of which the first ends 25 are angularly offset from one another and may not have the same value as the angle of which the first ends 24 are angularly offset from one another.
  • the angle ⁇ is also the angle of which the first ends 25 of the elastically flexible blades 23b are angularly offset from one another around the axis perpendicular to the plane P 4 and centered on the part d 'coupling 27.
  • the angle ⁇ is advantageously between 80 ° and 150 °.
  • the angle ⁇ is of the order of 120 °.
  • angles ⁇ between 80 ° and 150 ° are among the angles most unfavorable to the appearance of parasitic vibratory modes, that is to say of vibratory modes other than that in which the balance 6 oscillates angularly around its virtual pivot axis X 2 -X ' 2 , in the oscillation plane P 4 . It has been discovered that an angle ⁇ of the order of 120 ° gives the best results in terms of combating the appearance of the aforementioned parasitic vibration modes.
  • the balance 6 is pivotally mounted without resorting to a shaft retained and guided by two bearings, the friction at such bearings does not exist and the losses due to friction are greatly reduced, so that the mechanical oscillator 7 has a excellent quality factor.
  • the elastically flexible blades 23a are two in number. According to a variant not shown and not departing from the scope of the invention, more than two elastically flexible blades 23a could connect the mounting base 18 to the coupling part 27.
  • the elastically flexible blades 23b are two in number. According to a variant not shown and not going beyond the scope of the invention, more than two elastically flexible blades 23b could connect the coupling part 27 to the balance 6.
  • the balance 6 comprises two flat wings 28 that the cross member 21 connects to one another.
  • Each wing 28 carries a weight 16 and two weights 17.
  • These weights 16 and 17 have the function of increasing the inertia of the balance 6 relative to its pivot axis X 2 -X ' 2 .
  • the weights 17 are split rings reported and are distributed over the four vertices of a rectangle. As they can be pivoted on themselves, these weights 17 make it possible to modify the inertia of the balance 6 and thus to adjust the frequency of the mechanical oscillator 7.
  • the weights 16 and 17 may or may not be made of the same material.
  • the rest of the balance 6 is made of a material whose density is less than that (s) of the constituent material (s) of the weights 16 and 17. In this way, the ratio between the inertia of the balance 6 with respect to its axis pivot X 2 -X ' 2 and the weight of this balance 6 is high, so that the mechanical oscillator 7 is not very sensitive to shocks while having a high regulating power.
  • the barycenter of the balance 6 is located substantially on the virtual pivot axis X 2 -X ' 2 and at the level of the coupling part 27.
  • the inlet pallet 13 and the outlet pallet 14 are both rigid. They are also rigidly secured to the balance 6, insofar as the anchor 5 is rigidly fixed to the cross member 21, by means of two connecting pins 29 in the example shown.
  • downstream and upstream refer to the direction of progression of a tooth 15 at the level of the vanes 13 and 14.
  • Each pallet 13 or 14 comprises a rest surface 31 intended to temporarily stop each tooth 15 downstream, as well as an impulse surface 32 intended to receive an impulse from each tooth 15, that is to say say a thrust by which an energy for sustaining the oscillations of the mechanical oscillator 7 is transferred from the motor member of the barrel 1 to the mechanical oscillator 7.
  • Each rest surface 31 is formed by an upstream side of one of the pallets 13 and 14. Each rest surface 31 is curved in the direction of its length, so as to curl towards the other rest surface 31. Each surface rest 31 has a constant or substantially constant radius of curvature R 1 or R 2 , as well as a center of curvature located in a substantially fixed manner, on the virtual pivot axis X 2 -X ′ 2 .
  • Each impulse surface 32 is an end surface at the end of one of the vanes 13 and 14.
  • the mounting base 18, the elastically flexible blades 23a and 23b, as well as the balance 6 with the exception of the weights 16 and 17, are part of the same single piece made of a monocrystalline material, in particular in a monocrystalline material based on silicon or based on quartz.
  • this one-piece part is preferably predominantly made of silicon, in which case it advantageously has a surface layer of silicon oxide.
  • the mechanical oscillator 7 with the exception of the weights 16 and 17 can be cut from a silicon wafer, also called a wafer, by deep reactive ion etching, that is to say by implementing the method commonly called "DRIE" (acronym for "Deep Reactive Ion Etching"). It will be noted that the elastically flexible blades 23a and 23b are easily produced by means of this DRIE process.
  • the weights 16 and 17 can be metallic. In the example shown, they are made of gold.
  • the weights 16 can be obtained by galvanic growth.
  • the anchor 5 is a single piece made of a monocrystalline material, in particular of a monocrystalline material based on silicon or based on quartz.
  • the anchor 5 is preferably predominantly made of silicon, in which case it advantageously has a surface layer of silicon oxide.
  • the anchor 5 can be cut from a silicon wafer, also called a wafer, by deep reactive ionic etching, that is to say by implementing the process commonly called “DRIE”.
  • DRIE deep reactive ionic etching
  • the vanes 13 and 14 are advantageously coated with a coating having the function of reducing the coefficient of friction and increasing the resistance to wear. .
  • this coating may be in diamond, in particular in polycrystalline diamond, or in DLC (acronym for Diamond-Like Carbon), that is to say in carbon in the form of amorphous diamond, or else in grafen.
  • the teeth 15 of the escape wheel 11 can also be at least locally coated with such a coating having the function of reducing the coefficient of friction and increasing the resistance to wear.
  • the two assembly pegs 29 are made of a titanium alloy, for example of the Ti6Al4V alloy, and hold two elements assembled. having a silicon core, namely the cross member 21 and the anchor 5.
  • the mechanical oscillator 7 and / or the anchor 5 and / or the two assembly pegs 29 can be made of materials other than those mentioned above.
  • all or part of the mechanical oscillator 7 and / or of the anchor 5 can be produced using the “LiGA” process (acronym for “Lithographie, Galvanoformung und Abformung”).
  • all or part of the mechanical oscillator 7 and / or of the anchor 5 can be cut from a metal plate, by laser.
  • the adjustment mechanism 9 has a particularly simple constitution.
  • the same means namely the elastically flexible blades 23a and 23b, make both the anchor 5 and the balance 6 pivot. These means have an operation which produces no or practically no friction, as has been achieved. already mentioned previously.
  • an adjustment mechanism resulting from the association of a Swiss lever escapement and a mechanical oscillator with balance and hairspring has an operation in which friction takes place at the level of the bearings guiding the support shaft. anchor and at the bearings guiding the balance support shaft.
  • the return torque exerted by the elastically flexible blades 23a and 23b is substantially proportional to the angle at which the balance 6 is pivoted from its neutral position, around the virtual pivot axis X 2 -X ′ 2 . This helps to give a good isochronism to the mechanical oscillator 7.
  • the figures 6 to 9 each illustrate one of several states in which the adjustment mechanism 9 is successively found during its operation.
  • the angular amplitude of the oscillations of the balance 6 is preferably of the order of 6 degrees, which is the case in the example shown. This angular amplitude is compatible with the use of an escapement at rubbing rest such as the escapement 4.
  • the mechanical oscillator 7 is sized to oscillate at a frequency of the order of 25 Hz, which is the case in the example shown.
  • Other angular amplitudes and other oscillation frequencies can also be used without departing from the scope of the invention.
  • the balance 6 is angularly offset by an angle ⁇ , around its virtual pivot axis X 2 -X ' 2 , with respect to its neutral position. It pivots in the direction S 1 , towards its neutral position, under the effect of the return exerted by the elastically flexible blades 23a and 23b.
  • the input pallet 13 retains a tooth 15A of the teeth 12 and, in doing so, blocks the escape wheel 11 against the engine torque coming from the barrel 1.
  • this tooth 15A remains motionless or practically motionless, that is to say does not move or hardly moves upstream, in the direction of retreat, or downstream, in the direction of advance.
  • the balance 6 is angularly offset by an angle ⁇ , around its virtual pivot axis X 2 -X ' 2 , with respect to its neutral position. It pivots in the direction S 2 , towards its neutral position, under the effect of the return exerted by the elastically flexible blades 23a and 23b.
  • the output pallet 14 retains a tooth 15B of the toothing 12 and, in doing so, blocks the escape wheel 11 against the engine torque coming from the barrel 1.
  • this tooth 15B remains immobile or practically immobile, that is to say does not move or hardly moves upstream, in the direction of retreat, or downstream, in the direction of advance.
  • the engine torque coming from the barrel 1 does not or practically not interfere with the oscillations of the balance wheel 6, except during the impulse phases, that is to say during the phases during which the pulses I 1 and I 2 are applied.
  • the elastically flexible blades 23a and 23b can be arranged differently from one another, without departing from the scope of the invention.
  • they can be arranged as in the Swiss patent application CH 709 291 above, although the arrangement shown in figure 3 is advantageous for at least some of the aforementioned reasons.
  • the two elastically flexible blades may not cross each other, while being inclined with respect to each other so that, if these two elastically flexible blades each extend in the 'one of two planes, these two planes intersect, for example, at the level of the balance or of the mounting base.
  • a mechanism for adjusting an average speed according to the invention can be installed in a tourbillon.
  • the invention can be implemented in various timepieces. As it can have a small footprint, the invention can in particular be implemented in a watch such as a wristwatch.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Micromachines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (17)

  1. Mechanismus zur Einstellung einer mittleren Geschwindigkeit in einem Uhrwerk, umfassend ein Hemmungsrad (4) und einen mechanischen Oszillator (7), wobei der mechanische Oszillator (7) eine Unruh (6) und eine Vielzahl von elastisch flexiblen Klingen (23a, 23b) umfasst, welche elastisch flexibel in einer Schwingebene (P4) sind, und welche die Unruh (6) tragen und rückführen, so dass die Unruh (6) in einem Winkel in der Schwingebene (P4) schwingt,
    dadurch gekennzeichnet, dass er einen Anker (5) aufweist, welcher zwei starre Paletten (13, 14) umfasst, die starr mit der Unruh (6) verbunden und eingerichtet sind, um wechselweise mit einer Zahnung (12) des Hemmungsrads (11) zu kooperieren, wenn die Unruh (6) in einem Winkel schwingt, und wobei jede Palette (13, 14) eine vorgelagerte Seite aufweist, welche eine Ruhefläche (31) bildet, um sukzessive die Zähne (15) der Zahnung (12) in nachgelagerter Richtung entgegen eines Antriebmotormoments des Hemmungsrads (11) zu blockieren, wobei jede Palette (13, 14) eine Endfläche aufweist, welche eine Impulsfläche (32) bildet, um sukzessive Impulse der Zahnung (12) aufzunehmen.
  2. Einstellungsmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass jede Ruhefläche (31) in Richtung der anderen Ruhefläche (31) gekrümmt ist.
  3. Einstellungsmechanismus nach Anspruch 2, dadurch gekennzeichnet, dass jede Ruhefläche (31) in Richtung der anderen Ruhefläche (31) gekrümmt ist, um auf einem Zahn (15) der Zahnung (12), während einer Winkelschwingung der Unruh (6) gleiten zu können, wobei keine oder im Wesentlichen keine Drehbewegung des Hemmungsrads (11) verursacht wird.
  4. Einstellungsmechanismus nach einem der Ansprüche 2 und 3, dadurch gekennzeichnet, dass jede Ruhefläche (31) eine im Wesentlichen konstante Krümmung in seiner Längsrichtung aufweist und ein Krümmungszentrum hat, welches im Wesentlichen immer an der gleichen Stelle positioniert ist, im Wesentlichen an einer virtuellen Drehachse (X2-X'2) der Unruh (6).
  5. Einstellungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mechanische Oszillator (7) eine Befestigungsbasis (18) aufweist, wobei mindestens ein Teil der elastisch flexiblen Klingen (23a, 23b) jeweils ein Ende (24) umfassen, welches starr an der Befestigungsbasis (18) verbunden ist, wobei mindestens ein Teil der elastisch flexiblen Klingen (23a, 23b) je ein Ende (25) umfassen, welches starr an der Unruh (6) verbunden ist.
  6. Einstellungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mechanische Oszillator (7) eine Befestigungsbasis (18) umfasst, wobei mindestens eine erste und eine zweite elastisch flexible Klinge (23a) der elastisch flexiblen Klingen je zwei entgegengesetzte Enden aufweist, d.h. ein erstes Ende (24), welches starr an der Befestigungsbasis (18) verbunden ist und ein zweites Ende (26), wobei mindestens eine dritte und eine vierte elastisch flexible Klinge (23b) der elastisch flexiblen Klingen je zwei entgegengesetzte Enden aufweist, d.h. ein erstes Ende (25), welches starr mit der Unruh (6) verbunden ist und dass die zweiten Enden (26) der ersten, zweiten, dritten und vierten elastisch flexiblen Klingen (23a, 23b) mindestens starr miteinander verbunden sind.
  7. Mechanismus zur Einstellung einer mittleren Geschwindigkeit in einem Uhrwerk, umfassend ein Hemmungsrad (4) und einen mechanischen Oszillator (7), wobei der mechanische Oszillator (7) eine Unruh (6) und eine Vielzahl von elastisch flexiblen Klingen (23a, 23b) umfasst, welche elastisch flexibel in einer Schwingebene (P4) sind, und welche die Unruh (6) tragen und rückführen, so dass die Unruh (6) in einem Winkel in der Schwingebene (P4) schwingt,
    dadurch gekennzeichnet, dass er einen Anker (5) aufweist, welcher zwei starre Paletten (13, 14) umfasst, die starr mit der Unruh (6) verbunden und eingerichtet sind, um wechselweise mit einer Zahnung (12) des Hemmungsrads (11) zu kooperieren, wenn die Unruh (6) in einem Winkel schwingt, wobei der mechanische Oszillator (7) eine Befestigungsbasis (18) umfasst, mindestens eine erste und eine zweite elastisch flexible Klinge (23a) der elastisch flexiblen Klingen je zwei entgegengesetzte Enden aufweist, d.h. ein erstes Ende (24), welches starr an der Befestigungsbasis (18) verbunden ist und ein zweites Ende (26), mindestens eine dritte und eine vierte elastisch flexible Klinge (23b) der elastisch flexiblen Klingen je zwei entgegengesetzte Enden aufweist, d.h. ein erstes Ende (25), welches starr mit der Unruh (6) verbunden ist und wobei die zweiten Enden (26) der ersten, zweiten, dritten und vierten elastisch flexiblen Klingen (23a, 23b) zumindesten starr miteinander verbunden sind
  8. Einstellungsmechanismus nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass die zweiten Enden (26) der ersten, zweiten, dritten und vierten elastisch flexiblen Klingen (23a, 23b) starr miteinander durch ein Verbindungsstück (27) verbunden sind, wobei die ersten Enden (24) der ersten und zweiten elastisch flexiblen Klingen (23a) eines winkelig relativ zu dem anderen um einen Winkel (α) versetzt sind, welcher zwischen 80° und 150° liegt, bezogen auf eine Achse senkrecht zu der Oszillationsebene (P4) und zentriert auf dem Verbindungsstück (27), wobei die ersten Enden (25) der dritten und vierten elastisch flexiblen Klingen (23b) eines winkelig relativ zu dem anderen um einen Winkel (α) versetzt sind, welcher zwischen 80° und 150° liegt, bezogen auf eine Achse senkrecht zu der Oszillationsebene (P4) und zentriert auf dem Verbindungsstück (27).
  9. Einstellungsmechanismus nach Anspruch 8, dadurch gekennzeichnet, dass die ersten Enden (24) der ersten und zweiten elastisch flexiblen Klingen (23a) eines relativ zu dem anderen um einen Winkel (α) von 120° versetzt sind, bezogen auf die Achse senkrecht zur Oszillationsebene (P4) und zentriert auf das Verbindungsstück (27), wobei die ersten Enden (25) der dritten und vierten elastisch flexiblen Klingen (23b) eines winkelig relativ zu dem anderen um einen Winkel von 120° versetzt sind, bezogen auf die Achse senkrecht zur Oszillationsebene (P4) und zentriert auf das Verbindungsstück (27).
  10. Einstellungsmechanismus, nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass die zweiten Enden (26) der ersten, zweiten, dritten und vierten elastisch flexiblen Klingen (23a, 23b) starr miteinander durch ein Verbindungsstück (27) verbunden sind, durch welches eine virtuelle Drehachse (X2-X'2) der Unruh (6) verläuft.
  11. Einstellungsmechanismus nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, dass die zweiten Enden (26) der ersten, zweiten, dritten und vierten elastisch flexiblen Klingen (23a, 23b) starr miteinander durch ein Verbindungsstück (27) verbunden sind, wobei die Unruh (6) einen Schwerpunkt aufweist, welcher im Wesentlichen in dem Verbindungsstück (27) lokalisiert ist.
  12. Einstellungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mechanische Oszillator (7) eine Befestigungsbasis (18) umfasst, welche zwei Stoppelemente (20) aufweist, welche für die Unruh (6) Wegendanschläge sind und welche für die Unruh (6) eine maximale Winkelbahn dadurch definieren, dass die Unruh (6) daran gehindert wird, über die zwei entgegengesetzten Enden der maximalen Winkelbahn hinauszugehen.
  13. Einstellungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Unruh (6) zwei entgegengesetzte Flügel (28) und ein Steg (21) umfasst, welcher die beiden Flügel (28) miteinander verbindet, wobei mindestens ein Teil der elastisch flexiblen Klingen (23a, 23b) je ein Ende (25) umfassen, welches starr mit dem Steg (21) verbunden ist.
  14. Mechanismus zur Einstellung einer mittleren Geschwindigkeit in einem Uhrwerk, umfassend ein Hemmungsrad (4) und einen mechanischen Oszillator (7), wobei der mechanische Oszillator (7) eine Unruh (6) und eine Vielzahl von elastisch flexiblen Klingen (23a, 23b) umfasst, welche elastisch flexibel in einer Schwingebene (P4) sind, und welche die Unruh (6) tragen und rückführen, so dass die Unruh (6) in einem Winkel in der Schwingebene (P4) schwingt,
    dadurch gekennzeichnet, dass er einen Anker (5) aufweist, welcher zwei starre Paletten (13, 14) umfasst, die starr mit der Unruh (6) verbunden und eingerichtet sind, um wechselweise mit einer Zahnung (12) des Hemmungsrads (11) zu kooperieren, wenn die Unruh (6) in einem Winkel schwingt und wobei die Unruh (6) zwei entgegengesetzte Flügel (28) und einen Steg (21) umfasst, welcher die beiden Flügel (28) miteinander verbindet, wobei mindestens ein Teil der elastisch flexiblen Klingen (23a, 23b) je ein Ende (25) umfassen, welches starr mit dem Steg (21) verbunden ist.
  15. Einstellungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mechanische Oszillator (7) eine Befestigungsbasis (18) umfasst, wobei mindestens ein Teil der Befestigungsbasis (18), mindestens ein Teil der Unruh (6) und die elastisch flexiblen Klingen (23a, 23b) integral miteinander sind.
  16. Mechanismus zur Einstellung einer mittleren Geschwindigkeit in einem Uhrwerk, umfassend ein Hemmungsrad (4) und einen mechanischen Oszillator (7), wobei der mechanische Oszillator (7) eine Unruh (6) und eine Vielzahl von elastisch flexiblen Klingen (23a, 23b) umfasst, welche elastisch flexibel in einer Schwingebene (P4) sind, und welche die Unruh (6) tragen und rückführen, so dass die Unruh (6) in einem Winkel in der Schwingebene (P4) schwingt,
    dadurch gekennzeichnet, dass er einen Anker (5) aufweist, welcher zwei starre Paletten (13, 14) umfasst, die starr mit der Unruh (6) verbunden und eingerichtet sind, um wechselweise mit einer Zahnung (12) des Hemmungsrads (11) zu kooperieren, wenn die Unruh (6) in einem Winkel schwingt und wobei der mechanische Oszillator (7) eine Befestigungsbasis (18) umfasst, wobei mindestens ein Teil der Befestigungsbasis (18), mindestens ein Teil der Unruh (6) und die elastisch flexiblen Klingen (23a, 23b) integral miteinander sind.
  17. Uhrwerk, umfassend ein Antriebsorgan (1), ein Übersetzungsgetriebe (2), angetrieben von dem Antriebsorgan, dadurch gekennzeichnet, dass es einen Einstellungsmechanismus (9) nach einem der vorhergehenden Ansprüche umfasst, wobei das Hemmungsrad (11) von dem Übersetzungsgetriebe (2) angetrieben ist.
EP15200453.7A 2015-12-16 2015-12-16 Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk Active EP3182213B2 (de)

Priority Applications (7)

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ES15200453T ES2698115T3 (es) 2015-12-16 2015-12-16 Mecanismo de regulación de una velocidad media en un movimiento de relojería y movimiento de relojería
EP15200453.7A EP3182213B2 (de) 2015-12-16 2015-12-16 Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk
JP2018531329A JP2018537684A (ja) 2015-12-16 2016-12-15 クロックムーブメント内の平均速度調節機およびクロックムーブメント
PCT/EP2016/081132 WO2017102916A1 (fr) 2015-12-16 2016-12-15 Mécanisme de réglage d'une vitesse moyenne dans un mouvement d'horlogerie et mouvement d'horlogerie
US16/061,939 US20180372150A1 (en) 2015-12-16 2016-12-15 Mechanism for adjusting an average speed in a timepiece movement and timepiece movement
CN201680077919.8A CN108475039A (zh) 2015-12-16 2016-12-15 钟表机芯中用于调节平均速度的机构以及钟表机芯
HK18112680.0A HK1253383A1 (zh) 2015-12-16 2018-10-04 鐘錶機芯中用於調節平均速度的機構以及鐘錶機芯

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